CN103994096A - Hydraulic design method of no-jam cyclone pump - Google Patents

Abstract

The invention provides a hydraulic design method of a no-jam cyclone pump. An impeller of the cyclone pump is a semi-opening-type impeller, blades of the impeller include long blades and short blades, the lengths of the blades are different, due to the facts that the diameter of an outlet of the impeller of the cyclone pump, the width of the outlet of the impeller, the specific value range of the long blades and the short blades of the impeller are optimized and hydraulic design is carried out by controlling F8 section area selection and increasing the volute throat area, conveyed solid media are easy to pass, the passing rate of the conveyed solid media are improved, the blocking phenomena are prevented, meanwhile, loss of circulation flow in the cyclone pump is reduced, and accordingly efficiency of the cyclone pump is improved, and economic efficiency is good in production practices.

Description

A kind of Hydraulic Design Method without stopping up torque flow pump

Technical field

The present invention relates to a kind of torque flow pump Hydraulic Design Method, particularly a kind of Hydraulic Design Method without stopping up torque flow pump.

Background technique

Torque flow pump is the one of centrifugal pump, gains the name because its internal flow exists the vorticla motion of rotation.Torque flow pump is used for pumping complex dielectrics or impurity containing fluid, as the two-phase fluid containing rubbish, short fibre material.Internal Flow of Vortex Pump is very complicated, and blades retracted is rotated in the phyllocyst of the pump housing, and in the time of vane rotary, medium is increased by the effect energy of centrifugal force, enters interlobate medium and moved together with impeller by the promotion of blade.Near medium impeller outlet top has formed because centrifugal force is larger and has connected stream, medium at impeller middle part has formed circular flow, just because of the existence of circular flow, makes the hydraulic loss of pump larger, the efficiency of pump below 60%, causes the serious waste of the energy substantially.

Summary of the invention

For addressing the above problem, the invention provides a kind of Hydraulic Design Method without stopping up torque flow pump, by improving the several important parameters of impeller and strengthening volute throat area, adopt the structure of 2 linear leafs and 2 short blades, improve hydraulic performance and the reliability of torque flow pump.

The present invention realizes above-mentioned technical purpose by following technological means.

Without a Hydraulic Design Method of stopping up torque flow pump, it is characterized in that, the impeller of described torque flow pump is selected half-opened impeller, and the blade of described impeller comprises linear leaf, the short blade that several length differs, the structural parameter of the impeller of described torque flow pump: impeller outer diameter D ₂, impeller outlet width b ₂, impeller inlet diameter D _j, determine according to described torque flow pump rated point lift H, flow Q, rotation speed n, wherein,

Impeller outlet diameter

Impeller outlet width $b_2=0.66{\left(\frac{n_s}{100}\right)}^{5/6}{\left(\frac{Q}{n}\right)}^{1/3}$

Impeller inlet diameter $D_j=\sqrt{{K_0}^2{\left(\frac{Q}{n}\right)}^{2/3}+D_h^2}$

In formula:

D ₂-impeller outlet diameter, m;

B ₂-impeller outlet width, m;

D _j-impeller inlet diameter, m;

The rated lift of H-pump, m;

G-gravity accleration, m/s ²;

N-rotating speed, r/min;

β ₂-impeller outlet laying angle, span is 20 °～90 °;

-head coefficient, span is 0.65～0.85;

Q-design discharge, m ³/ s;

N _sthe specific speed of-design conditions, span 80～180;

K ₀-impeller inlet velocity coefficient, span 3.6～4.85;

D _h-hub diameter, m.

Preferably, the length L of described linear leaf ₁length L with short blade ₂ratio be

Preferably, described impeller inlet velocity coefficient K ₀value 3.95.

Preferably, described impeller inlet velocity coefficient K ₀value 4.85.

Preferably, the thickness of the thickness rate linear leaf of described short blade is large, and being equal in weight of linear leaf and short blade.

Preferably, the quantity of described linear leaf, short blade is 2, and described 2 linear leafs and 2 short blades are alternately and be uniformly distributed.

Preferably, volute throat area F, the F of described torque flow pump ₈cross-sectional area has following formula to determine:

Volute throat area $F=(1.35~1.65)\frac{Q}{K_{v_t}\sqrt{2\mathrm{gH}}}$

F ₈cross-sectional area $A_8=\frac{Q}{k_3\sqrt{2\mathrm{gH}}}$

In formula:

-velocity coefficient;

K ₃-velocity coefficient, chooses according to Oleg Stepanov curve;

Area Ratio span is 1.15～1.25.

Hydraulic Design Method without stopping up torque flow pump of the present invention, can effectively improve described torque flow pump and connect stream, fed sheet of a media is more easily passed through, there is good hydraulic performance, the structural type being combined with of linear leaf, short blade simultaneously, ensureing under the prerequisite of the normal work of torque flow pump, effectively reducing the energy loss of circular flow in pump chamber, improving the efficiency of described torque flow pump.Pass through F ₈the design of volute throat area is chosen and strengthened to cross-sectional area, improves the passing rate of conveying solid substance medium, promotes the efficiency of torque flow pump, has good economic benefit in production practices.

Brief description of the drawings

Fig. 1 is the blade structure figure of the impeller of torque flow pump of the present invention.

Fig. 2 is described impeller axis projection.

Description of reference numerals is as follows:

1-linear leaf, 2-short blade, 3-wheel hub, 4-back shroud of impeller.

Embodiment

Below in conjunction with accompanying drawing and specific embodiment, the present invention is further illustrated, but protection scope of the present invention is not limited to this.

Hydraulic Design Method without stopping up torque flow pump of the present invention, the impeller of described torque flow pump as shown in Figure 1 and Figure 2, is selected half-opened impeller, comprises blade, wheel hub 3, back shroud of impeller 4, described blade is arranged on a side of back shroud of impeller 4, and described wheel hub 3 is positioned at the center of back shroud of impeller 4.Linear leaf, short blade that several length that adopts described blade differs, to improve pump internal flow situation, improve hydraulic performance and the reliability of torque flow pump.Concrete, the length L of described linear leaf ₁length L with short blade ₂ratio be the quantity of described linear leaf, short blade is 2, and in order to keep impeller balance, described 2 linear leafs and 2 short blades are alternately and be uniformly distributed.Preferably, make the thickness of thickness rate linear leaf of described short blade large, and being equal in weight of linear leaf and short blade.

The structural parameter of the impeller of described torque flow pump: impeller outer diameter D ₂, impeller outlet width b ₂, impeller inlet diameter D _j, determine according to described torque flow pump rated point lift H, flow Q, rotation speed n, specific as follows:

$b_2=0.66{\left(\frac{n_s}{100}\right)}^{5/6}{\left(\frac{Q}{n}\right)}^{1/3};$

$D_j=\sqrt{{K_0}^2{\left(\frac{Q}{n}\right)}^{2/3}+D_h^2};$

In formula:

The rated lift of H-pump, m;

G-gravity accleration, m/s ²;

N-rotating speed, r/min;

β ₂-impeller outlet laying angle, span is 20 °～90 °;

-head coefficient, span is 0.65～0.85;

Q-design discharge, m ³/ s;

N _sthe specific speed of-design conditions, span 80～180;

K ₀-impeller inlet velocity coefficient, span 3.6～4.85;

D _h-hub diameter, m.

Volute throat area F, the F of described torque flow pump ₈cross-sectional area has following formula to determine:

Volute throat area $F=(1.35~1.65)\frac{Q}{K_{v_t}\sqrt{2\mathrm{gH}}}$

F ₈cross-sectional area $A_8=\frac{Q}{k_3\sqrt{2\mathrm{gH}}}$

In formula:

-velocity coefficient;

K ₃-velocity coefficient, chooses according to Oleg Stepanov curve;

Area Ratio span is 1.15～1.25.

The present invention carries out the Hydraulic Design by controlling the several important parameters of impeller, coordinates F simultaneously ₈eighth section area choose and strengthen throat opening area, avoid torque flow pump to stop up thereby reach, the object that the efficiency of pump is improved.In production practices, there is good economic benefit.

Described embodiment is preferred embodiment of the present invention; but the present invention is not limited to above-mentioned mode of execution; in the situation that not deviating from flesh and blood of the present invention, any apparent improvement, replacement or modification that those skilled in the art can make all belong to protection scope of the present invention.

Claims (7)

1. the Hydraulic Design Method without obstruction torque flow pump, it is characterized in that, the impeller of described torque flow pump is selected half-opened impeller, linear leaf (1), short blade (2) that several length that comprises the blade of described impeller differs, the structural parameter of the impeller of described torque flow pump: impeller outer diameter D ₂, impeller outlet width b ₂, impeller inlet diameter D _j, determine according to described torque flow pump rated point lift H, flow Q, rotation speed n, wherein,

Impeller outlet diameter

Impeller outlet width $b_2=0.66{\left(\frac{n_s}{100}\right)}^{5/6}{\left(\frac{Q}{n}\right)}^{1/3}$

Impeller inlet diameter $D_j=\sqrt{{K_0}^2{\left(\frac{Q}{n}\right)}^{2/3}+D_h^2}$

In formula:

D ₂-impeller outlet diameter, m;

B ₂-impeller outlet width, m;

D _j-impeller inlet diameter, m;

The rated lift of H-pump, m;

G-gravity accleration, m/s ²;

N-rotating speed, r/min;

β ₂-impeller outlet laying angle, span is 20 °～90 °;

-head coefficient, span is 0.65～0.85;

Q-design discharge, m ³/ s;

N _sthe specific speed of-design conditions, span 80～180;

K ₀-impeller inlet velocity coefficient, span 3.6～4.85;

D _h-wheel hub (3) diameter, m.

2. the Hydraulic Design Method without stopping up torque flow pump according to claim 1, is characterized in that the length L of described linear leaf (1) ₁length L with short blade (2) ₂ratio be

3. the Hydraulic Design Method without stopping up torque flow pump according to claim 1, is characterized in that described impeller inlet velocity coefficient K ₀value 3.95.

4. the Hydraulic Design Method without stopping up torque flow pump according to claim 1, is characterized in that described impeller inlet velocity coefficient K ₀value 4.85.

5. the Hydraulic Design Method without stopping up torque flow pump according to claim 1, it is characterized in that, the thickness of the thickness rate linear leaf (1) of described short blade (2) is large, and being equal in weight of linear leaf (1) and short blade (2).

6. the Hydraulic Design Method without stopping up torque flow pump according to claim 5, it is characterized in that, the quantity of described linear leaf (1), short blade (2) is 2, and described 2 linear leafs (1) and 2 short blades (2) are alternately and be uniformly distributed.

7. according to the Hydraulic Design Method without obstruction torque flow pump described in claim 1-6 any one, it is characterized in that volute throat area F, the F of described torque flow pump ₈cross-sectional area has following formula to determine:

Volute throat area $F=(1.35~1.65)\frac{Q}{K_{v_t}\sqrt{2\mathrm{gH}}}$

F ₈cross-sectional area $A_8=\frac{Q}{k_3\sqrt{2\mathrm{gH}}}$

In formula:

-velocity coefficient;

K ₃-velocity coefficient, chooses according to Oleg Stepanov curve;

Area Ratio span is 1.15～1.25.